Shaft assembly

ABSTRACT

A telescopable shaft assembly has at least two shaft elements capable of sliding in one another as an internal shaft element and an outer shaft element connected to one another in torque transmitting manner via at least one sliding splined portion. An axial fixation defines predetermined breaking point between the shaft elements. The axial fixation becomes ineffective once a predetermined impact force acting in a telescoping direction is reached. The shaft elements are movable relative to one another, once the axial fixation has become ineffective, in low-friction manner along the sliding splined portion under the action of the impact force. When the axial fixation is effective, an annular gap is formed between a splined portion runout on a free end of the outer shaft element and an unsplined portion of the inner shaft element. The annular gap, at least in the area of the free end of the outer shaft element, is at least partially filled with a sealant.

CROSS-REFERENCE TO RELATED APPLICATIONS

This is a continuing application, under 35 U.S.C. § 120, of copendinginternational application PCT/EP2005008975, filed Aug. 19, 2005, whichdesignated the United States; this application also claims the priority,under 35 U.S.C. § 119, of German patent application DE 10 2004 043621.5, filed Sep. 7, 2004; the prior applications are herewithincorporated by reference in their entirety.

BACKGROUND OF THE INVENTION Field of the Invention

The invention relates to a telescoping shaft assembly with at least twoshaft elements capable of sliding in one another. The two elements forman internal shaft element on the one hand and an outer shaft element onthe other hand, and they are connected to one another in torquetransmitting manner via at least one sliding splined portion. An axialfixation is provided in the manner of a predetermined breaking pointbetween the shaft elements. The axial fixation becomes ineffective oncea predetermined impact force acting in the direction of telescoping isreached. The shaft elements are movable relative to one another, oncethe axial fixation has become ineffective, in low-friction manner alongthe sliding splined portion under the action of the impact force.

Shaft assemblies of the generic type are described, for example, in U.S.Pat. Nos. 6,279,221 and 6,193,612. In this connection, reference is alsohad to a publication entitled “slip-in-tube universal-joint shaft”technology (12th Aachen Colloquium “Automobile and Engine Technology”,2003, pp. 1485-95). One object of the shaft assembly described thereinis to optimize collapse behavior in the event of a crash. To this end,it is proposed that, in the event of telescoping due to an accident,impact energy is at least partially absorbed by purposeful deformation.This is achieved, for example, by an inner shaft element being drivenout of the splined portion into a tapered zone of an outer shaftelement. Movement into the tapered zone brings about forced deformationof the inner shaft element, which ultimately results in thefragmentation of the end region of the inner shaft element.

SUMMARY OF THE INVENTION

It is accordingly an object of the invention to provide a shaftassembly, which overcomes the above-mentioned disadvantages of theheretofore-known devices and methods of this general type and whichprovides for a shaft assembly by way of which it is possible, inparticular for all-wheel drive vehicles, to reduce the loads to whichoccupants are exposed in frontal-impact accidents.

With the foregoing and other objects in view there is provided, inaccordance with the invention, a telescopable shaft assembly,comprising:

at least two shaft elements capable of sliding in one another, the shaftelements including an internal shaft element and an outer shaft element;

at least one sliding splined portion connecting the two shaft elementsto one another in a torque transmitting manner;

an axial fixation forming a predetermined breaking point between theshaft elements, the axial fixation becoming ineffective once apredetermined impact force acting in a telescoping direction is reached;

the shaft elements being movable relative to one another, once the axialfixation has become ineffective, in low-friction manner along thesliding splined portion under action of the impact force;

the outer shaft element having a free end formed with a splined portionrunout and the inner shaft element is formed with an unsplined portion;

wherein, when the axial fixation is effective, an annular gap is formedbetween the splined portion runout on the outer shaft element and theunsplined portion of the inner shaft element; and

a sealant at least partially filling the annular gap, at least in anarea of the free end of the outer shaft element.

In contrast with the previous design philosophy with purposeful energyabsorption during collapse of the telescopable shaft elements undercrash conditions, it is now proposed according to the invention that anaxial fixation designed for normal operation of the vehicle be provided,which fixation becomes ineffective in the event of a vehicle accident,thus for example fractures, tears, shears or the like, once apredetermined impact force is reached. Once this axial fixationconfigured in the manner of a predetermined breaking point has becomeineffective, it no longer prevents the shaft elements from telescopinginto one another, but instead permits low-friction telescoping of theshaft elements under the action of the impact force. A typical order ofmagnitude for design of the axial fixation may be a limit force of forexample 5 to 40 kN (kilonewtons). If, in the event of a crash, theimpact force reaches this predetermined limit force, the axial fixationis nullified and the impact force is thus opposed by a lower resistance.

The term “low-friction” as used herein is to be understood to mean thateven forces of less than 50% to 10% of the designed limit force for theaxial fixation are sufficient to move the shaft elements relative to oneanother.

A shaft assembly designed in this manner, in particular for a frontcardan shaft (i.e., propshaft) in an all-wheel drive vehicle with atransverse, front-mounted engine, is advantageous because dispensingwith deformation in the shaft assembly does not give rise to any hazarddue to components snapping or breaking away. Any intrusion of suchcomponents into the passenger compartment is thus reliably avoided.

The axial fixation itself may preferably also be used at the same timeto ensure exact alignment of the shaft axes with one another.Advantageously, such exact alignment is achieved, for example, by pressfitting between the tooth tip and tooth root in the splined portion ofat least one of the two shaft elements.

In order to increase the service life of shaft assemblies according tothe invention, it is moreover provided that a seal is inserted into anannular gap arising between the shaft elements, which seal may, forexample, assume the form of a sealing ring or a formless sealant of thepaste or gel type. The sealant itself may take the form of an adhesive,which thus simultaneously assumes the axial fixation function.Additionally or alternatively, axial fixation may also be provided by aninsert which may be fitted between the two shaft elements, the insertlikewise preferably being associated with a sealing element.

To ensure an extended life of the entire shaft assembly, the splinedportion is preferably introduced by cold forming, for example coldrolling.

In accordance with an added feature of the invention, the axial fixationis formed by an adhesive bond and/or weld and/or calking and/or acombination of shear elements and/or frictional portions in the slidingsplined portion and/or the like.

In accordance with an additional feature of the invention, the annulargap is sealed by the sealant. In accordance with an additional featureof the invention, the sealant is a sealing ring or a formless sealant ofthe sealing cord, paste or gel type.

In an alternative embodiment, there is provided at least one bead formedin the sliding splined portion, the bead establishing a predeterminedforce/travel profile over a displacement path for the displacing impactforce, once the axial fixation has become unfastened.

In accordance with another feature of the invention, the dimensions ofthe bead or beads are selected such that the displacement force exhibitsa declining profile over the displacement path.

In accordance with a further feature of the invention, the outer shaftelement comprises a taper on its end remote from the inner shaftelement, by means of which taper it is possible to limit movement,determined by an impact force, of the inner shaft element within theouter shaft element in the manner of a limit stop.

In accordance with again an added feature of the invention, the innershaft element comprises an unsplined portion on its end remote from theouter shaft element, the external diameter of which unsplined portion issmaller than the root diameter of the splined portion of the outer shaftelement to permit unimpeded movement of the outer shaft element throughthe inner shaft element.

In accordance with again an additional feature of the invention, for thepurpose of torque transmission, the splined portions of the shaftelements are arranged relative to one another virtually withoutbacklash.

In accordance with again another feature of the invention, on the innershaft element, the diameter of the root circle of the splined portion isgreater than the external diameter of the unsplined portion of the innershaft element following on from the splined portion.

In accordance with again a further feature of the invention, the splinedportion of the inner shaft element runs out in open manner at its endfacing the outer shaft element.

In accordance with a concomitant feature of the invention, on the outershaft element, the internal diameter of the unsplined portion is greaterthan the tip diameter on the splined portion of the inner shaft element.

Other features which are considered as characteristic for the inventionare set forth in the appended claims.

Although the invention is illustrated and described herein as embodiedin shaft assembly, it is nevertheless not intended to be limited to thedetails shown, since various modifications and structural changes may bemade therein without departing from the spirit of the invention andwithin the scope and range of equivalents of the claims.

The construction and method of operation of the invention, however,together with additional objects and advantages thereof will be bestunderstood from the following description of specific embodiments whenread in connection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a typical installation situation for a shaft assemblyaccording to the invention in a vehicle;

FIG. 2 shows, taking a cardan shaft by way of example, a shaft assemblyaccording to the invention before assembly;

FIG. 3 shows the shaft assembly according to FIG. 2 in the assembledstate;

FIG. 4 shows a plan view of a portion indicated with dashed lines inFIG. 3;

FIG. 5 shows, in a partial section, the internal view of two assembledshaft elements;

FIG. 6 shows a cutout of the portion shown with a continuous line inFIG. 5;

FIG. 7 shows a first longitudinal bead in one of the splines and furtheraxial fixations in FIGS. 7A and 7B;

FIG. 8 shows a view according to section VIII-VIII in FIG. 7;

FIG. 9 shows another axial fixation by means of press fitting betweentooth tip and tooth root; and

FIG. 10 shows another axial fixation by way of an insert.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring now to the figures of the drawing in detail and first,particularly, to FIG. 1 thereof, there is seen a schematic diagram of avehicle 1, also showing the essential elements of the drive train,including an internal combustion engine 2, a transmission 3, adifferential 4, a front propshaft or cardan shaft 5, a rear propshaft orcardan shaft 22, a rear differential 23 together with universal-jointshafts and wheels, which have not been assigned reference numerals. Thepreferred implementation for the invention is in this case the frontcardan shaft 5, the structure of which will now be explained in greaterdetail.

FIG. 2, for example, illustrates the primarily important elements of thefront cardan shaft 5, including an inner shaft element 5 i, with aninner splined portion 6 i, and an outer shaft element 5 a, with an outersplined portion 6 a. The splined portions 6 i and 6 a, also referred toas toothed shafts, together form the sliding splined portion 6, orsliding toothed shaft 6, visible in FIG. 3. The tubular shaft element 5a comprises a taper 7 for connection to a joint or flexible disk. Theinner shaft element 5 i, which preferably here also takes the form of ahollow tube, comprises on its end remote from the sliding splinedportion 6 a connection flange 8 for connection to a joint or flexibledisk. The configuration of the sliding splined portion 6 is, however,here primarily important to the invention, with FIG. 4 showing a planview of the splined portion 6 a.

Splined portion runouts 9 and 10 are primarily important to the splinedportion 6 a, which runouts are technically particularly straightforwardto manufacture and, in particular in the area of the splined portionrunout 9, also facilitate assembly for the inner shaft element 5 i whichis to be slid in. Beneath the splined portion runout 9, an annular gap12 is obtained together with a portion 11, here unsplined, of the innershaft element 5 i, which annular gap, at least in the area of a free end5 e of the outer shaft element 5 a, is at least partially filled with asealant 13. At the free end, which has not been assigned a referencenumeral, of the inner shaft element 5 i, the splined portion 6 i ends inopen manner and is thus particularly easy to produce, for example bycold forming such as cold rolling.

The sketch in FIG. 6 clarifies the manner in which, after the axialfixation has been nullified, low-friction telescoping of the shaftelements 5 a and 5 i is possible. Accordingly, for example for the innershaft element 5 i, the external diameter DIA of the unsplined portion 11is less than the root diameter DAF on the outer shaft element 6 a.Correspondingly, the diameter DAI within the outer shaft element 5 a isgreater than the tip diameter DIK on the inner shaft element 5 i and theroot diameter DAF on the outer shaft element is greater than the rootdiameter DIF on the inner shaft element 5 i. These design featuresensure low-friction relative movements between the shaft elements 5 iand 5 a, the extent of which movement may be limited by a taper 26acting as an axial limit stop on the outer shaft element 5 a. Thedistance of this taper 26 is selected such that, even at maximumdisplacement of the sliding splined portion 6, this limit stop is notreached, unless the shaft assembly were disassembled.

Examples of an axial fixation shown in FIG. 7 are beads 14 and 15 whichhave here been produced in the manner of a longitudinal bead, forexample by calking, impact extrusion, rolling or pressing or the like.These longitudinal beads 14, 15 in the inner shaft element 5 i causeindentations and, arising therefrom, undercuts 16, 17 in the outer shaftelement 5 a, such that axial fixation is achieved by means of thiscombination of interlocking and frictional connection. By way ofkinematic reversal, such beads may, however, also be embossed from theoutside into the outer shaft element 5 a, such that a comparableretaining action is obtained. The virtual absence of backlash indicatedin FIG. 7 between the tooth faces 18, 19 on the one hand and 20, 21 onthe other hand is also of particular significance to the shaft assemblyaccording to the invention. In this manner, it is ensured that the frontcardan shaft 5 does not clatter (because circumferential and tiltingbacklash are minimized) or suffer unnecessary wear and, in the event oftelescoping of the shaft elements 5 a, 5 i due to an accident, guidancein a defined manner is achieved. Circumferential backlash of 0 to 0.5 mmbetween the tooth faces 18, 19 and 20, 21 respectively for shaftdiameters of between 60 mm and 70 mm is preferred for this virtuallybacklash-free design.

Additionally or alternatively to the beads 14, 15, it is also possibleto provide spots or extensive areas of curable plastics, adhesives orwelds 25 (see FIG. 7 a) and/or shearing pins 24 (see FIG. 7 b). As africtional connection variant, longitudinal beads 14′ are alsoconceivable which may be integrally formed or applied in the area of thetooth root (see FIG. 9) or in the areas of the tooth tip (not shownhere).

FIG. 10 shows an insert 27 as a further embodiment of an axial fixation,which is here fastened to the shaft element 5 a and bears via a clampingmember 28 and a sealing element 29 against the inner shaft element 5 i.In this case too, kinematic reversal may be considered with regard tofastening the insert and the sealing and clamping functions. Dependingon the design, undercuts or grooves may additionally be provided in theshaft elements 5 a, 5 i in order to ensure defined axial fixations andsealing conditions.

The beads 14, 14′, 15 may be selected with regard to their length, widthand height/depth or cross-sectional form in such a manner that, on theone hand, a defined limit force may be established and, on the otherhand, a very specific characteristic curve may also be predeterminedover the displacement path of the sliding splined portion 6. Accordingto the invention, this characteristic curve of the displacement forceexhibits a predominantly declining profile over the displacement path,such that no negative effects on the occupants accommodated in thevehicle 1 are to be anticipated on the part of the front cardan shaft 5.A distinction may be drawn between a first phase, in which, once theaxial fixation has been nullified, the sliding splined portion 6 isstill in engagement and predetermined force/travel profiles areaccordingly established, and a second phase, in which the splinedportions 6 i and 6 a are no longer in engagement, such that the shaftelements 5 i, 5 a slide past one another in virtually undamped manner.According to the invention, both phases are designed to be low-friction.At least the first phase exhibits the declining force/travel profile. Inthe second phase, the profile may optionally also be constant or riseslightly to a low level, but without regaining the force level of thefirst phase.

In order to establish a specific characteristic curve, the beads mayalso be arranged as transverse beads distributed around thecircumference. In an embodiment as longitudinal bead, it is possible toprovide a continuous profile (see FIG. 8) or a segmented assembly of aplurality of beads in succession.

In an assembly with a plurality of beads, it is also possible for atleast one of the beads to be provided as a clamping bead for axialfixation and other beads to be designed to predetermine a specificcharacteristic curve over the displacement path. These beads may beassigned to the inner and/or outer shaft element 5 i or 5 a.

The characteristic curve may be established by varying not only theshape of the longitudinal beads but also the radial distribution thereofaround the circumference of the shaft elements 5 i and/or 5 a.

Those skilled in the pertinent art will readily understand that the useof the shaft assembly according to the invention is not limited to thevehicle concept shown in FIG. 1, but it may also be selected for otherdrive configurations, for example with a continuous cardan shaft.

1. A telescopable shaft assembly, comprising: at least two shaftelements capable of sliding in one another, said shaft elementsincluding an internal shaft element and an outer shaft element; at leastone sliding splined portion connecting said two shaft elements to oneanother in a torque transmitting manner; an axial fixation forming apredetermined breaking point between said shaft elements, said axialfixation becoming ineffective once a predetermined impact force actingin a telescoping direction is reached; said shaft elements being movablerelative to one another, once said axial fixation has becomeineffective, in low-friction manner along said sliding splined portionunder action of the impact force; said outer shaft element having a freeend formed with a splined portion runout and said inner shaft element isformed with an unsplined portion; wherein, when said axial fixation iseffective, an annular gap is formed between said splined portion runouton said outer shaft element and said unsplined portion of said innershaft element; and a sealant at least partially filling said annulargap, at least in an area of said free end of said outer shaft element.2. The shaft assembly according to claim 1, wherein said axial fixationis formed by one or more fixing means selected from the group consistingof an adhesive bond, a weld, a calking, a combination of shear elements,and frictional portions in said sliding splined portion.
 3. The shaftassembly according to claim 1, wherein said sealant is configured toseal said annular gap.
 4. The shaft assembly according to claim 3,wherein said sealant is a sealing ring.
 5. The shaft assembly accordingto claim 3, wherein said sealant is a formless sealant selected from thegroup consisting of a sealing cord, a sealing paste, and a gel sealant.6. A telescopable shaft assembly, comprising: at least two shaftelements capable of sliding in one another, said shaft elementsincluding an internal shaft element and an outer shaft element; at leastone sliding splined portion connecting said two shaft elements to oneanother in a torque transmitting manner; an axial fixation forming apredetermined breaking point between said shaft elements, said axialfixation becoming ineffective once a predetermined impact force actingin a telescoping direction is reached; said shaft elements being movablerelative to one another, once said axial fixation has becomeineffective, in low-friction manner along said sliding splined portionunder action of the impact force; and at least one bead formed in saidsliding splined portion, said bead establishing a predeterminedforce/travel profile over a displacement path for the displacing impactforce, once said axial fixation has become unfastened.
 7. The shaftassembly according to claim 6, wherein said at least one bead hasdefined dimensions selected such that a displacement force exhibits adeclining profile over the displacement path.
 8. The shaft assemblyaccording to claim 6, wherein said axial fixation is formed by one ormore fixing means selected from the group consisting of an adhesivebond, a weld, a calking, a combination of shear elements, and frictionalportions in said sliding splined portion.
 9. The shaft assemblyaccording to claim 6, wherein said outer shaft element is formed with ataper on on an end thereof remote from said inner shaft element, saidtaper forming a limit stop configured to limit movement, determined byan impact force, of said inner shaft element within said outer shaftelement.
 10. The shaft assembly according to claim 6, wherein said innershaft element is formed with an unsplined portion on an end thereofremote from said outer shaft element, said unsplined portion having anouter diameter smaller than a root diameter of said splined portion ofsaid outer shaft element, permitting unimpeded movement of said outershaft element through said inner shaft element.
 11. The shaft assemblyaccording to claim 6, wherein said splined portions of said shaftelements are configured for torque transmission substantially withoutbacklash.
 12. The shaft assembly according to claim 6, wherein a rootcircle of said splined portion on said inner shaft element has adiameter greater than an external diameter of an unsplined portion ofsaid inner shaft element following on from said splined portion.
 13. Theshaft assembly according to claim 6, wherein said splined portion ofsaid inner shaft element runs out in open manner at an end thereoffacing said outer shaft element.
 14. The shaft assembly according toclaim 6, wherein said outer shaft element is formed with an unsplinedportion having an inner diameter greater than a tip diameter on saidsplined portion of said inner shaft element.